Beverage dispensing apparatus

ABSTRACT

A beverage dispensing device for dispensing pressurized beverages at a high flow rate without producing excessive foaming comprising a streamlined valve assembly and a downward extending nozzle assembly which permits a range of containers to be filled from the bottom.

CROSS REFERENCE TO RELATED APPLICATION

This application is a divisional of U.S. patent application Ser. No.10/388,907, entitled “Beverage Dispensing Apparatus,” filed on Mar. 13,2003, the contents of which are incorporated herein by reference.

BACKGROUND OF THE INVENTION

The present invention relates to an apparatus for dispensing carbonatedor pressurized beverages, and more specifically to an apparatus fordispensing carbonated or pressurized beverages at high flow rates withminimal foaming.

Pressurized beverages, such as beer, are produced in a manner that thebeverage contains a certain amount of dissolved gas, typically carbondioxide (CO₂). While a certain amount of dissolved CO₂ occurs naturallyin the beer brewing and fermentation process, most large commercialbreweries dissolve additional CO₂ into their product. Adding additionalCO₂ serves two main purposes for the commercial breweries. First, from aquality control standpoint, all the beer produced can be modified tocontain the same amount of CO₂. Second, the additional CO₂ gives thebeer a more effervescent quality, which is perceived by the consumer ashaving better crispness and flavor.

Beer produced by most major breweries contains between 10 and 15 psi(68950 and 103425 Newtons per square meter) of dissolved CO₂. Sinceatmospheric levels of CO₂ are substantially smaller, beer has a tendencyto release some of its dissolved CO₂ when exposed to the ambientatmosphere. Due to the complex chemical makeup of beer, foam tends toform when this dissolved CO₂ comes out of solution.

Additional parameters contributing to the amount of foam occurring inbeer include temperature and turbulence. The physical properties ofliquids dictate that the higher the liquid temperature, the lower itscapacity for dissolved gasses. Thus, the greater the temperature ofbeer, the greater the tendency for its dissolved gasses to come out ofsolution and the greater the tendency of the beer to foam. Turbulenceand other forms of agitation produce regions of sudden, extreme pressurevariation within the beer that cause CO₂ to come out of solution in theform of foam.

While much of the beer produced by the major commercial breweries tendsto be packaged in bottles and cans, a large volume of beer is alsopackaged in large, sealed containers known as kegs. Kegs are reusableand refillable aluminum containers that allow for efficient, sanitaryhandling, storage and dispensing of typically 15.5 gallons (58.7 liters)of beer. Beer packaged into kegs, called keg beer, is commonly served atbars, taverns, night clubs, stadiums, festivals and large parties.

Dispensing keg beer into open containers for consumption requiresspecialized equipment. The beer dispensing faucet (commonly called thebeer tap) comprises a valve and a spout for controlling and directingthe flow of beer into an open container. Beer often foams as it isdispensed from conventional faucets. One cause of such foaming is simplythe pressure differential between CO₂ dissolved in the beer and CO₂present in the ambient atmosphere; CO₂ will naturally be released fromthe beer when the beer is exposed to the atmosphere. Another cause ofsuch foaming is the turbulent nature by which beer is dispensed fromconventional faucets; even when dispensed carefully, beer splashes ontothe walls and bottom of the container and foam results.

A small amount of foam is often desirable. Beer that has not been storedproperly often loses its dissolved CO₂ to the atmosphere and isconsidered to be flat. Thus, a small amount of foam indicates to theconsumer that the beer is fresh. Additionally, beer marketers have beensuccessful in portraying the perfect container of beer as possessing afrothy layer of foam. On the other hand, too much foam is undesirable tothe consumer and the beverage vendor. Since foam fills up a containerwith CO₂ instead of with liquid beer, excessive amounts of foam leavethe consumer dissatisfied, often to the point of requesting a newcontainer be served. Knowing this, vendors are left with two choices.They can partially fill a container, wait for the foam to dissipate andthen add additional beer, a time-consuming process. Alternatively, theycan pour out excess foam as they are filling the container, wasting beerin the process.

Since excessive foaming is problematic for both the consumer and thevendor, attempts have been made to design beer dispensing systems thatare installed and configured in a manner that ideally achieves optimalamounts of foam in the dispensing process. In addition to maintainingthe beer at a constant, cold temperature throughout the dispensingprocess, conventional beer dispensing systems are configured to pourbeer at a slow enough flow rate that beer exits the faucet at a velocitythat does not cause foaming when the beer impacts the container.

Conventional systems are optimized for a flow rate of one U.S. gallon(3.785 liters) per minute. While such a flow rate is suitable for mostlow-volume dispensing applications, there are many situations in whichit would be beneficial for both the vendor and the consumer if beercould be dispensed more quickly while still maintaining optimal amountsof foam. At busy bars, taverns, festivals, large parties and stadiums,consumers often must wait in long lines before being served. Under thesecircumstances, it would be desirable for both the vendor and theconsumer for beer to be dispensed more quickly.

Previous beer dispensing systems have been designed to dispense beermore quickly than the standard one U.S. gallon per minute flow rate. Onedrawback with these systems is that they typically employ elaborateelectronic control mechanisms, making them expensive to manufacture andmaintain. Additionally, some of these systems employ the use of areservoir near the point of the faucet making the devices large anddifficult to clean. Moreover, the retrofit of such devices onto existingbar tops can be difficult and expensive.

SUMMARY OF THE INVENTION

The present invention is directed to a beverage dispensing device fordispensing pressurized beverages at a flow rate substantially higherthan prior mechanical tap apparatus without producing excessive foaming.It can be implemented as a purely mechanical device so as to keepmanufacturing and maintenance costs low. In addition, the presentinvention can be implemented without the use of reservoirs at or nearthe point of dispensing, thus facilitating cleaning and retrofitting toexisting bar tops.

In a preferred embodiment, the present invention comprises a beveragedispensing apparatus for dispensing a pressurized beverage comprising anozzle through which the pressurized beverage at least initially exitsat atmospheric conditions having an internal passageway, a liquidreceiving end adapted to attach as the end element of a pressurizedbeverage dispensing system, and a liquid dispensing end that dispensesthe pressurized beverage at least initially to atmospheric conditions,wherein the cross-sectional area of the internal passageway of thenozzle decreases from the liquid receiving end to the liquid dispensingend.

In another embodiment, the present invention comprises an upwardextending neck, a streamlined valve assembly and a downward extendingnozzle assembly. The overall shape and size of the device permits arange of containers to be filled from the bottom. Additionally, thenozzle assembly contains a streamlined flow redirecting component thatserves to generally radially disperse liquid flow. Thus, the amount offoaming that occurs when beer is dispensed at fast rates is desirablyreduced.

In one embodiment, the horizontal cross-sectional area of the nozzlegradually decreases from the top of the nozzle to the bottom or liquiddispensing end of the nozzle. Preferably, the profile of this decreasingcross-sectional area is consistent with that of a liquid stream fallingunder the force of gravity in the absence of such a nozzle. A nozzlewith this shape ensures that liquid flowing through it remains insubstantially continuous contact with the interior wall of the nozzle.In this way, air from the liquid dispensing end of the nozzle isprevented from bubbling up into the nozzle. Additionally, the viscousforces acting between the nozzle interior wall and the liquid flowingthrough the nozzle serve to counteract the acceleration experienced bythe liquid in the nozzle due to gravitational forces.

In another embodiment of the invention, flow-straightening elements areadded to the nozzle which serve to make the flow of liquid through thenozzle less turbulent. Such elements also increase the amount of surfacearea across which decelerating viscous forces can take effect.

In another embodiment of the invention, the device is able toselectively dispense beer at two different flow rates. In such anembodiment a pressure-reducing element is integrated into the devicealong with a multi-way valve that selectively routes liquid through thepressure-reducing element. When the valve is positioned such that liquidfirst flows through the pressure reducer before entering the rapidbeverage dispensing device, liquid is dispensed at a reduced rate,preferably the optimal rate of conventional beer dispensing faucets.When the valve is positioned such that liquid bypasses the pressurereducer, the rapid beverage dispensing device functions at its fasterflow rate.

Because the rapid beverage dispensing device is capable of dispensingbeer at at least twice the flow rate of conventional beer dispensingsystems while still achieving optimal levels of foam, it also tends toattract attention from beverage consumers as an object of curiosity.This attraction can be heightened by forming components of the devicefrom transparent material to allow consumers to see the beverage flowingtherein.

Further advantages and features of the embodiments of the presentinvention will be apparent from the following detailed description ofthe invention in conjunction with the associated drawings.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a side elevation view showing the components of a beveragedispensing system with a schematic sectional view of the firstembodiment of the rapid beverage dispensing device.

FIG. 2 is a close-up schematic sectional view of the rapid beveragedispensing device of FIG. 1.

FIG. 3 is a schematic perspective view of a second embodiment of therapid beverage dispensing device where the neck assembly is replaced bya tall draft dispensing tower.

FIG. 4 is a close-up schematic sectional view of the valve assembly ofFIG. 2 with the valve shown in the closed position.

FIG. 5 is a side elevation view of another embodiment of a streamlinedvalve member for use in the valve assembly of FIG. 2.

FIG. 6 shows a side elevation view of yet another embodiment of astreamlined valve member for use in the valve assembly of FIG. 2.

FIG. 7 is a sectional schematic view of the valve assembly of FIG. 4with the valve shown in the open position.

FIG. 8 is a perspective view of the streamlined valve member of FIG. 4illustrating the curvature and overall shape of the liquid-facingsurface of the valve shoulder.

FIG. 9 is a cross sectional perspective view of the valve neck and valveshoulder.

FIG. 10 is a schematic sectional view of a conventional beer dispensingfaucet.

FIG. 11 is an illustration of the gravitational effects on liquidflowing from a conventional faucet.

FIG. 12 shows a schematic sectional view of another embodiment of thenozzle assembly where the parabolic profile of the nozzle crosssectional area of FIG. 2 is approximated by nozzle with a linear taper.

FIG. 13 shows a schematic sectional view of another embodiment of thenozzle assembly where the parabolic profile of the nozzle crosssectional area of FIG. 2 is approximated by a cylindrical nozzle.

FIG. 14 is a perspective sectional view of yet another embodiment of thenozzle assembly where the nozzle contains four semicircularflow-straightening channels.

FIG. 15 is a sectional view of a nozzle assembly containing twosemicircular flow-straightening channels.

FIG. 16 is a sectional view of a nozzle assembly containing sixsemicircular flow-straightening channels.

FIG. 17 is a sectional view of a nozzle assembly containing sevencircular flow-straightening channels.

FIG. 18 is a close-up, sectional schematic view of the nozzle assemblyof FIG. 2 with a container present and liquid flow lines indicating themanner in which the flow redirector redirects liquid flow.

FIG. 19 is a perspective view of the flow redirector of FIG. 2.

FIG. 20 is sectional view of another embodiment of the flow redirectorfor use in the nozzle assembly of FIG. 2.

FIG. 21 is a sectional view of still another embodiment of the flowredirector for use in the nozzle assembly of FIG. 2.

FIG. 22 is a sectional view of yet another embodiment of the flowredirector for use in the nozzle assembly of FIG. 2.

FIG. 23 is a schematic sectional view of a nozzle assembly with a flowredirector whose position can be longitudinally adjusted.

FIG. 24 is a schematic sectional view of the nozzle assembly of FIG. 23with the flow redirector shown moved to a new position.

FIG. 25 is a schematic sectional view of the rapid beverage dispensingdevice containing a conical diffuser within its neck assembly.

FIG. 26 is a schematic sectional view of the rapid beverage dispensingdevice shown with a multi-way valve and a pressure reducing element.

FIG. 27 is a close-up, schematic sectional view of the multi-way valveof FIG. 26 shown with the valve routing liquid in a manner that bypassesthe pressure-reducing element.

FIG. 28 is a close-up, schematic sectional view of the multi-way valveof FIG. 26 shown with the valve routing liquid through thepressure-reducing element prior to directing liquid to the rapidbeverage dispensing device.

DETAILED DESCRIPTION OF PREFERRED EMBODIMENTS OF THE INVENTION

As shown in FIG. 1, the rapid beverage dispensing device 35 comprises aneck assembly 36, a valve assembly 37, and a downward-extending nozzleassembly 38. In a preferred embodiment, neck assembly 36 issubstantially vertical. The rapid beverage dispensing device 35 isdesigned to attach to a conventional pressurized beverage dispensingsystem, such as a beer dispensing system 39 that includes a beer keg 40or similar beverage-containing reservoir and beverage tubing 41 forconveying a beverage from a container or beer keg 40 to the rapidbeverage dispensing device 35. A shank 42 connects the rapid beveragedispensing device 35 to beverage tubing 41. Keg tapping device 43connects beverage tubing 41 to beer keg 40. Draft dispensing tower 44supports shank 42.

Beer produced by most major manufacturers in the United States isformulated to be stored and served optimally at approximately 38 degreesFahrenheit (3.3 degrees Celsius). If the beer is warmer than thisoptimal temperature, it will tend to release too much carbon dioxide(CO₂) when it is dispensed. If the beer is colder than this optimaltemperature, it will tend to retain too much CO₂ when it is dispensedand have a muted flavor. Since most systems are not able to maintain aprecise temperature, a range between 36 and 40 degrees Fahrenheit (2.2and 4.4 degrees Celsius) is generally considered acceptable.Accordingly, in one embodiment, the beer dispensing system 39 of thepresent invention has the ability to cool various elements of the systemand maintain these elements within this acceptable temperature range.

As shown in FIG. 1, in many dispensing systems beer in the beveragetubing 41 is kept cold by circulating a cold liquid through coolanttubing 45 bundled with beverage tubing 41. Such systems typicallyinvolve refrigerating and circulating glycol through means of a glycolrefrigeration device 46 and a glycol pump 47. Alternatively, somesystems blow cold air through conduits containing the beverage tubing 41as a means of keeping the beverage tubing 41 cold.

Beer contained in a beer keg 40 requires an energy source for conveyingthe beverage from the beer keg 40 through the entire beer dispensingsystem 39 to the rapid beverage dispensing device 35. Such energy iscommonly provided via pressurized gas, typically pressurized CO₂. Asshown in FIG. 1 in these systems, a tank 48 containing pressurized CO₂is connected to beer keg 40 via a pressurized gas hose 49. Pressureregulating device 50 serves as a means to adjust the pressure of the CO₂driving the beer through the beer dispensing system 39. In systems wherea large distance exists between the beer keg 40 and the rapid beveragedispensing device 35, a second gas may be used to provide added pressurefor moving the beer through the beverage tubing 41. Pressurized nitrogen(N₂) housed in nitrogen tank 51 may be used as this second gas. Nitrogentank 51 is connected to beer keg 40 via a separate pressurized gas hose49. A separate pressure regulating device 50 serves as a means to adjustthe additional pressure provided by the compressed nitrogen. Somesystems are able to extract nitrogen from the air, precluding the needfor a separate nitrogen tank. Optionally, in another embodiment, asystem may use a mechanical pump (not shown) to provide the energyrequired to move beer through the system in lieu of, or in addition to,pressurized gas.

The Reynolds number is a dimensionless parameter often used in fluidflow analysis. Fluid moving through round piping or tubing possessing aReynolds number under 2100 is said to exhibit laminar flow. A systemwith a Reynolds number greater than 4000 is said to exhibit turbulentflow. A system that is neither laminar nor turbulent is said to exhibittransitional flow characteristics. The Reynolds number can be calculatedusing the following equation: ${Re} = \frac{\rho\quad{VD}}{\mu}$

where Re=Reynolds number

ρ=density of the liquid

V=linear velocity of the liquid

D=diameter of the tubing

μ=viscosity of the liquid

The pressure drop experienced by liquid moving through the rapidbeverage dispensing device 35 is one of several parameters thatdetermine the flow rate at which beer moves through the beer dispensingsystem 39. The flow rate is also influenced by the length, diameter androughness of the beverage tubing 41, the height differential between thebeer keg 40 and the rapid beverage dispensing device 35, and the energyprovided by the pressurized CO₂ and/or N₂. In particular, for fullydeveloped laminar liquid flow, the flow rate can be determined accordingto the following equation:$Q = \frac{\pi\quad D^{4}\quad\Delta\quad p}{128\quad\mu\quad l}$

where Q=volumetric flow rate

D is the diameter of the beverage tubing 41

Δp=the pressure differential between the beer keg 40 and the rapidbeverage dispensing device 35

μ=the viscosity of the beer or other liquid being dispensed

l=the length of beverage tubing 41 through which the beer flows

While the target flow rate for conventional beer dispensing faucets isone U.S. gallon (3.785 liters) per minute, the rapid beverage dispensingdevice 35 has a target flow rate of at least twice that rate. Regardlessof whether beer is flowing at one gallon per minute or three gallons perminute, for beverage tubing 41 possessing an inside diameter of under 1inch, flow through the beverage tubing 41 is rarely completely laminar.Under these circumstances, the following equation applies:$h_{L} = {f\quad\frac{l}{D}\frac{V^{2}}{2\quad g}}$

where

h_(L)=head loss between sections 1 and 2 of the system

f=friction factor (function of beverage tubing 41 roughness and Reynoldsnumber)

l=length of beverage tubing 41

D=diameter of beverage tubing 41

V=linear velocity of the fluid

g=gravitational constant

Accordingly, as the beverage tubing 41 connecting the beer keg 40 to therapid beverage dispensing device 35 is lengthened and the diameter ofthe beverage tubing 41 is decreased, the amount of energy required fromthe pressurized CO₂ and/or N₂ must increase in order to overcome theadditional pressure head loss. Additionally, the amount of energyrequired from the pressurized CO₂ must increase in order to increase thevelocity of the liquid moving through the beverage tubing 41.Preferably, the beer dispensing system 39 is configured to deliver beerat an increased flow rate to the point of the shank 42 permitting therapid beverage-dispensing device 35 to provide increased pouringcapacity compared with conventional systems.

Neck assembly 36 of the rapid beverage dispensing device 35 positionsand supports the rapid beverage dispensing device 35 in a manner thatallows for the bottom filling of a wide variety of container sizes,ranging from glasses to pitchers. To accommodate the bottom filling ofsuch containers, the distance between the distal end 52 of nozzleassembly 38 and the top of a bar 53 or other structure directly beneathit is preferably at least as great as the height of the largestcontainer to be filled. Preferably, there should be substantialclearance to allow a pitcher 54 to be placed directly beneath the nozzleassembly 38.

One embodiment of the rapid beverage dispensing device 35 of the presentinvention is shown in more detail in FIG. 2. In the embodiment shown inFIG. 2, the lower end 55 of the neck assembly 36 has threads 56 toattach to a standard beer faucet shank 42 using a standard shankcoupling nut 57, compression ring 58 and compression washer 59, althoughother methods of attachment, including but not limited to flanges withO-rings and quick-disconnect fittings are contemplated. Additionally,neck assembly 36 may be permanently attached to shank 42 by welding orother means. In a common bar-top installation, shank 42 is attached to adraft dispensing tower column 60. A coupling gasket 61 is positionedbetween the shank 42 and the neck assembly 36 to ensure a tight seal.Within neck assembly 36 is a length of neck tubing 62 for conveyingliquid from the shank bore 63 to the valve assembly 37. The diameter ofthe neck tubing 62 preferably matches the diameter of the shank bore 63at the point of attachment between neck assembly 36 and shank 42.Preferably, neck tubing 62 at the lower end 55 of the neck assembly 36is initially aligned axially with the shank bore 63. In this embodiment,neck tubing 62 has about a 90 degree bend before continuing verticallywithin neck assembly 36. Neck tubing 62 then bends through an arc 64 ofabout 90 degrees near the upper end 65 of the neck assembly 36.Turbulence associated with a change in direction of liquid flow isreduced as the radius of the arc 64 increases. While an arc 64 with alarge radius would decrease the turbulence associated with changing thedirection of liquid flow, it would also result in the rapid beveragedispensing device 35 having a large horizontal distance between thedraft dispensing tower 44 and the nozzle assembly 38. Accordingly, theradius of arc 64 is preferably small enough for the nozzle assembly 38to be positioned directly over the bar-top drain 66. In a preferredembodiment, valve assembly 37 is attached to the upper end 65 of theneck assembly 36 such that liquid is able to move through the necktubing 62 and into the valve assembly 37 without leakage. Additionally,neck tubing 62 in the upper end 65 of the neck assembly 36 may increasein inside diameter as it approaches the valve assembly 37 such that theinside diameter of the neck tubing 62 matches the inside diameter of thevalve housing 94 at the point where the neck assembly 36 and the valveassembly 37 are joined.

Because neck assembly 36 is exposed to the ambient environment, beerresiding in the neck tubing 62 during period of system inactivity canbecome undesirably warm. To maintain beer in the neck tubing 62 at anappropriate serving temperature, neck assembly 36 may be filled withinsulation 67. In lieu of, or in addition to insulation 67, the neckassembly 36 may be cooled with glycol by extending coolant tubing 45into neck assembly 36 (not shown).

As shown in FIG. 3, in another embodiment of this invention, the neckassembly 36 of the rapid beverage dispensing device 35 is replaced witha tall draft dispensing tower assembly 68 consisting of a tall draftdispensing tower column 69, a draft dispensing tower cover 70, a draftdispensing tower base 71, mounting screws 72, a shank 42, and columninsulation 73. In this embodiment, the valve assembly 37 attaches to ashank 42 affixed to the tall draft dispensing tower column 69. Valveassembly 37 may be attached to shank 42 using shank coupling nut 57,compression ring 58, compression washer 59, and coupling gasket 61,although other means, including flanges with O-rings andquick-disconnect fittings, are contemplated. The distance between thebar top 53 and the shank 42 is such that the distance between the distalend 52 of the nozzle assembly 38 and the bar top 53 is greater than theheight of a standard pitcher 54. In this embodiment, no neck assembly isexposed to the ambient atmosphere and beer maintained at pressureupstream from the valve assembly 37 remains insulated from the ambientatmosphere within the tall draft dispensing tower assembly 68.Additionally, in this embodiment, the diameter of the shank bore 63 maygradually increase along its length such that, at one end, the diameterof the shank bore 63 is equal to the diameter of the beverage tubing 41,and that the diameter of the shank bore 63 matches the inside diameterof the valve housing 94 at the point where the valve assembly 37attaches to the shank 42.

In one embodiment, shown in FIG. 4, valve assembly 37 comprises valvemember 74, handle lever 75, friction ring 76, bonnet washer 77,compression bonnet 78, valve chamber 79, valve seat 80, valve shoulderguide 81, exterior air vent hole 82 and interior air vent hole 83. Valvemember 74 may comprise valve head 84, valve neck 85, valve shoulder 86,and seat washer 87. Valve neck 85 may be affixed to valve head 84 by anymeans known. Preferably, valve neck 85 is affixed to valve head 84 by athreaded means such that the two parts can be dissembled. Seat washer 87may be held in place between valve head 84 and valve neck 85. Theoverall shape of the assembled valve head 84, seat washer 87 and valveneck 85 is streamlined so as to minimally disturb the liquid flowingaround it. Accordingly, the liquid-facing outer surface 88 of seatwasher 87 is contoured to blend smoothly, preferably tangentially, withthe outer surface 89 of the valve head 84. Additionally, theliquid-facing outer surface 88 of the seat washer 87 is contoured toblend smoothly, preferably tangentially with valve neck 85.

Other embodiments of valve member 74 are shown in FIG. 5 and FIG. 6. Inthese embodiments, valve head 84 is generally spherical or elliptical innature, the outer surface 88 of seat washer 87 is contoured to generallyblend smoothly with the outer surface 89 of the valve head 84. Also, theouter surface 88 of seat washer 87 is contoured to generally blendsmoothly into the valve neck 85. As shown in FIG. 4, valve shoulder 86may be sized to slide longitudinally into the valve shoulder guide 81with a tight circumferential tolerance so as to keep the entire valvemember 74 aligned axially with respect to the valve chamber 79. Thedistal end 90 of handle lever 75 fits into the valve shoulder slot 91. Aball joint 92 built into the handle lever 75 nests in the ball seat 93that is part of the valve housing 94. A friction ring 76 and bonnetwasher 77 fit circumferentially around the top of ball joint 92. Acompression bonnet 78 may also fit circumferentially around the handlelever 75 and is held in place via threads in the compression bonnet 78and threads built into the valve housing 94. When threaded into place,compression bonnet 78 pushes against the friction ring 76 and the bonnetwasher 77 forming a seal that prevents beer from leaking out of thevalve assembly 37 through the ball seat 93.

FIG. 4 illustrates the valve assembly 37 with the valve member 74 in theclosed position. In this position, the proximal, threaded end 95 ofhandle lever 75 may be angled toward valve head 84. Since handle lever75 pivots about its ball joint 92, in this valve-closed position, thedistal end 90 of the handle lever 75 is angled away from the valve head84, pulling the valve member 74 longitudinally until the seat washer 87comes into contact with the valve seat 80, forming a seal that cuts offthe flow of liquid. In this position, liquid in the valve chamber 79 andthroughout the system will likely be at a pressure greater than theambient atmospheric pressure to prevent CO₂ from coming out of solutionwhile the system is not pouring beer. Accordingly, pressure from theliquid in the valve chamber 79 combined with the frictional forcesacting between the valve shoulder 86 and the valve shoulder guide 81 andamong the valve shoulder slot 91, the friction ring 76, the bonnetwasher 77, the compression bonnet 78 and the handle lever 75 aresufficient to hold the valve member 74 in its closed position.Consequently, despite the pressure of the liquid upstream of the valvemember 74, no springs, locks, actuators or other components applying anactive force to the valve member 74 are required to maintain the valvemember 74 in its closed position. Additionally, with the valve member 74in the closed position, the valve shoulder slot 91 completes a channelbetween the exterior air vent hole 82 and the interior air vent hole 83allowing air to enter the upper part of the nozzle 99 to facilitate morerapid and complete draining of any liquid in the nozzle assembly 38 themoment the valve member 74 is moved into the closed position.

To open the valve member 74, the threaded end 95 of the handle lever 75is moved forward, in a direction generally away from the valve seat 80.As the handle lever 75 is moved in this manner, it pivots within theball seat 93 about the center of its ball joint 92 causing the distalend 90 of the handle lever 75 to rotate in an opposite direction. Thismovement of the distal end 90 of the handle lever 75 serves to slide thevalve member 74 in a direction that moves the seat washer 87 away fromthe valve seat 80, thereby placing the valve member 74 in the openposition. Forces acting on the valve head 84 from the liquid flowingaround it combined with frictional forces acting between the valveshoulder 86 and the valve shoulder guide 81 and among the valve shoulderslot 91, the friction ring 76, the bonnet washer 77, the compressionbonnet 78 and the handle lever 75 are sufficient to hold the valvemember 74 in its open position without the need to apply a continuousactive force to the handle lever 75 or valve member 74.

Preferably, disturbances to liquid flow are minimized by a valveassembly 37 which is as streamlined as possible. As illustrated by theliquid flow lines 96 in FIG. 7, liquid flowing through the valveassembly 37 is guided in an arcing manner into the nozzle assembly 38which is oriented in a generally downward direction. Accordingly, thevalve assembly 37 must not only serve to start and stop the flow ofliquid, but also to guide the liquid into the nozzle 99 while causing aslittle liquid flow disturbance as possible. As shown in FIG. 8, tofacilitate a smooth redirection of liquid flow, the liquid-facingsurface 97 of the valve shoulder 86 is contoured to match the curvatureof the interior surface of the valve housing 94 when the valve member 74is in its open position. In particular, in the embodiment shown here,the interior surface of the valve housing 94 near the valve shoulder 86is generally the shape of a portion of an arced cylinder. That is, theliquid-facing surface 97 of the valve shoulder 86 is generally concavein shape and posses two radii of curvature. The first radius matches thelarge radius of the arc formed by the valve housing 94 that guides theliquid into the nozzle 99. The second radius of curvature isperpendicular to the first and matches the inside radius of the valvehousing 94 at the point where the valve assembly 37 and the nozzle 99are joined. Alternatively, the liquid-facing surface 97 of the valveshoulder 86 may possess only the first radius of curvature, in whichcase the liquid-facing surface 97 of the valve shoulder 86 will stilldirect liquid flow in a streamlined manner into the nozzle 99.Additionally, the liquid-facing surface 97 of the valve shoulder 86 mayalso be planar, in which case the edges of such a plane should be flushwith the interior surface of the valve housing 94 when the valve member74 is in its open position and the plane sloped in a manner toefficiently direct liquid flow into the nozzle 99. In contrast, asillustrated in FIG. 10, the liquid-facing surface 97 of a valve shoulder86 found in a conventional beer dispensing faucet 98 is blunt andgenerally vertically planar. Furthermore, such a design results inliquid that is abruptly redirected as indicated by liquid flow lines 96.Such abrupt redirection of liquid can cause turbulence.

Since some of the liquid flowing through the valve chamber 79 must passthe valve neck 85 on its way into the nozzle assembly 38, the crosssection of the valve neck 85, illustrated in FIG. 9, is streamlined forliquid flow in this direction.

Alternatively to the above described embodiment, which assumes manualmovement of the valve member 74, the energy required to move the valvemember 74 between its open and closed positions may be provided by anautomatic or motor-operated means. For instance, in one embodiment, alinear actuator connected to the valve shoulder 86 may replace thefunction of the pushing and pulling of the handle lever 75 in moving thevalve member 74 from its closed position to its open position and back.Additionally, the valve member 74 may be moved via electromagneticmeans, in a manner similar to the solenoids used to control water flowin household appliances. Also, a geared or other rotary valve movementmechanism may also function to move the valve member 74 between itsclosed and open positions. Energy for rotating such gears may beprovided by electromechanical or manual means.

Preferably, liquid flowing through valve assembly 37 is directedimmediately into the nozzle assembly 38, as shown in FIG. 2. Preferably,nozzle assembly 38 comprises a downward-extending nozzle 99 and a liquiddispersion member or flow redirector 100 positioned near the lower end101 of nozzle 99. Liquid flowing past the valve assembly 37 into thenozzle assembly 38 will tend to accelerate due to the effects ofgravity. Nozzle assembly 38 fulfills four primary functions. First,viscous forces acting between the nozzle interior surface 102 and theliquid serve to slow the velocity of the liquid flow, somewhatcounteracting the acceleration of the liquid due to gravity. Second, thenozzle interior surface 102 is shaped so as to minimize the chance ofair moving up into the system when valve member 74 is in its openposition. A solid, air-free liquid stream serves to minimize foaming ofthe liquid within the nozzle assembly 38. Third, the flow redirector 100serves to redirect the flow of liquid exiting the nozzle assembly 38 ina manner that minimizes the turbulence and foaming caused when theliquid impacts the inside surface of the container being filled.Preferably, nozzle assembly 38 is long enough so that the flowredirector 100 is able to reach the bottom of the largest container tobe dispensed, allowing for the filling of containers at or near theirbottoms. In a preferred embodiment, nozzle assembly 38 is from about 3inches (7.62 cm) to about 15 inches (38.1 cm) in length. Morepreferably, nozzle assembly 38 is from about 4 inches (10.16 cm) toabout 12 inches (30.48 cm) in length. Still more preferably, nozzleassembly 38 is from about 8 inches (20.32 cm) to 10 inches (25.4 cm) inlength.

A liquid stream 103 flowing from a conventional faucet 98 is shown inFIG. 11. In the absence of a nozzle 99, the velocity of liquid exitingfaucet 98 increases as the liquid falls due to gravity. Thisacceleration results in a decreasing cross sectional area of the liquidstream 103 as the liquid falls farther and farther away from the faucet98. The general shape of this profile is parabolic and its specificprofile depends on the flow rate of the liquid and the diameter of thefaucet outlet 104. Using Bernoulli's equation along with basic geometry,the cross sectional area of the liquid stream 103 at a given distancefrom the faucet outlet 104 can be calculated. According to Bernoulli'sequation:${p_{1} + {\frac{1}{2}\rho\quad V_{1}^{2}} + {\rho\quad g\quad z_{1}}} = {p_{2} + {\frac{1}{2}\rho\quad V_{2}^{2}} + {\rho\quad g\quad z_{2}}}$

where ρ₁, ρ₂ is the liquid pressure at the faucet outlet 104 and at somegiven distance from the faucet outlet 104, respectively

ρ is the density of the liquid

V₁, V₂ is the linear velocity of the liquid stream 103 at the faucetoutlet 104 and at some given distance from the faucet outlet 104,respectively

g is the acceleration due to gravity

z₁ and z₂ refer to points at the faucet outlet 104 and some givendistance from the faucet outlet 104, respectively

Since a free flowing liquid stream 103 is at atmospheric pressure,ρ₁=ρ₂=0. Setting z₁=0, z₂=h and renaming V₂ as V₀ _(and V) ₁ as V_(h)provides as equation for V_(h) in terms of h, where V_(h) is the linearvelocity of the liquid stream 103 at a vertical distance, h, beneath thefaucet outlet 104. $\begin{matrix}{{0 + {\frac{1}{2}\rho\quad V_{h}^{2}} + {\rho\quad g*0}} = {0 + {\frac{1}{2}\quad\rho\quad V_{0}^{2}} + {\rho\quad g\quad h}}} \\{{\frac{1}{2}\rho\quad V_{h}^{2}} = {{\frac{1}{2}\rho\quad V_{0}^{2}} + {\rho\quad g\quad h}}} \\{V_{h}^{2} = {V_{0}^{2} + {2\quad g\quad h}}} \\{V_{h} = \sqrt{V_{0}^{2} + {2\quad g\quad h}}}\end{matrix}$

where V₀ is the linear velocity of the liquid stream 103 at the faucetoutlet 104.

The flow rate of a liquid stream 103 can be related to the liquid stream103 linear velocity and the liquid stream 103 cross sectional areaaccording to the following equation:Q=A₀V₀

where Q is the flow rate of the liquid

A₀ is the cross sectional area of the faucet outlet 104

V₀ is the linear velocity of the liquid stream 103 at the faucet outlet104.

Solving for V₀ and substituting in the equation for V_(h) yields thefollowing:$V_{h} = \sqrt{\left( \frac{Q}{A_{0}} \right)^{2} + {2\quad g\quad h}}$

For a circular faucet outlet 104, A₀ can be expressed in terms of D₀,the diameter of the faucet outlet 104: $\begin{matrix}{A_{0} = {\pi\left( \frac{D_{0}}{2} \right)}^{2}} \\{A_{0} = \frac{\pi\quad D_{0}^{2}}{4}}\end{matrix}$

One more substitution solves for V_(h) in terms of D₀: $\begin{matrix}{V_{h} = \sqrt{\left( \frac{Q}{\frac{\pi\quad D_{0}^{2}}{4}} \right)^{2} + {2\quad g\quad h}}} \\{V_{h} = \sqrt{\left( \frac{4Q}{\pi\quad D_{0}^{2}} \right)^{2} + {2\quad g\quad h}}} \\{V_{h} = \sqrt{\frac{16\quad Q^{2}}{\pi^{2}D_{0}^{4}} + {2\quad g\quad h}}}\end{matrix}$

Additionally, since the flow rate of the liquid is constant throughout acompressionless system:Q=A_(h)V_(h)

where Q is the volumetric flow rate of the liquid

A_(h) is the cross sectional area of the liquid stream 103 at a distanceh from the faucet outlet 104

V_(h) is the linear velocity of the liquid stream 103 at a distance hfrom the faucet outlet 104

Solving the above for A_(h) and substituting in the previous definitionof V_(h), the cross sectional area of the liquid stream 103, A_(h), canbe determined as a function of its vertical distance h from the faucetoutlet 104, the diameter of the faucet outlet 104 and the liquid flowrate: $\begin{matrix}{Q = {V_{h}A_{h}}} \\{\quad{\overset{\Cap}{..}\quad..}} \\{A_{h} = \frac{Q}{V_{h}}} \\{A_{h} = \frac{Q}{\sqrt{\frac{16\quad Q^{2}}{\pi^{2}\quad D_{0}^{4}} + {2\quad g\quad h}}}}\end{matrix}$

Preferably, the cross sectional area profile of the nozzle assembly 38matches the cross sectional area profile of a free-falling liquid stream103, as calculated using the above equation. In this embodiment, thecross sectional area of the nozzle 99 gradually decreases from top tobottom. In a preferred embodiment, where a flow redirector is used,nozzle 99 widens near its distal end to accommodate the flow redirector100, but the cross sectional area of the resulting concentric annuluspreserves the continuity of this gradually decreasing cross sectionalarea to the point of the nozzle assembly outlet 105. As shown, theconcentric annulus maintains this gradually decreasing cross sectionalarea through the use of a flow director whose flow redirector shaft 106gradually increases in cross sectional area from top to bottom.Alternatively, the flow redirector 100 may have a flow redirector shaft106 of constant diameter if the distal end of the nozzle 99 were to havea gradually decreasing cross section (not shown). A nozzle assembly 38with a cross sectional area profile that matches the profile of a freefalling liquid stream 103 serves to keep the liquid flowing through thenozzle assembly 38 in constant contact with the nozzle interior surface102. In this manner, viscous forces acting between the liquid and thenozzle interior surface 102 serve to decelerate the liquid.Additionally, air is unable to bubble up into the nozzle assembly 38 aslong as the liquid is flowing at the flow rate for which the nozzleassembly 38 is optimized.

In an alternative embodiment of the nozzle assembly 38, shown in FIG.12, a nozzle 107 with a linear taper approximates the graduallydecreasing cross sectional area of nozzle 99 with a cross-sectional areaprofile that matches that of a free-flowing liquid stream.

In another embodiment of the nozzle assembly 38, shown in FIG. 13, acylindrical nozzle 108 is used. In this embodiment, the cross sectionalarea of the cylindrical nozzle 108 is constant until the flow redirector100 is introduced in which case the decrease in cross-sectional area dueto the positioning of the flow redirector 100 is sufficient to preventair from entering the cylindrical nozzle 108 while liquid is flowing.Thus, the cross sectional area of the internal passageway decreases fromthe liquid receiving end of the nozzle to the liquid dispensing end ofthe nozzle.

In still another embodiment, shown in FIG. 14, the nozzle assembly 38contains two or more flow-straightening channels 109 that serve toreduce any lateral movement of liquid in the nozzle assembly 38 anddecrease the turbulence of liquid flowing through the nozzle assembly38. Preferably, nozzle 99 is subdivided into at least two channels 109,and preferably three to ten channels 109. More preferably, nozzle 99 isdivided into four equally sized channels 109. FIG. 15, FIG. 16 and FIG.17 illustrate, in cross-section, various embodiments of a channelednozzle.

The Reynolds number provides an indication as to the laminar orturbulent nature of liquid flow. The Reynolds number for a nozzle 99 ofcircular cross-section without flow-straightening channels 109 can beexpressed as follows: ${Re} = \frac{\rho\quad{VD}}{\mu}$

The Reynolds number for a non-circular conduit can be determined fromthe following equation: ${Re}_{h} = \frac{\rho\quad{VD}_{h}}{\mu}$

where Re_(h) is the Reynolds number based on the hydraulic diameter. Thehydraulic diameter is defined as D_(h)=4A/P where A is thecross-sectional area of the conduit and P is the perimeter of theconduit. For each equally sized, semicircular, wedge-shaped channel 109in the nozzle assembly 38: $\begin{matrix}{A = {{\frac{1}{n}{\pi\left( \frac{D}{2} \right)}^{2}} = {\frac{1}{n}{\pi\left( \frac{D^{2}}{4} \right)}}}} \\{{4A} = {{4\left( \frac{1}{n} \right)\pi\frac{D^{2}}{4}} = \frac{\pi\quad D^{2}}{n}}} \\{P = {{{2\left( {\frac{1}{2}D} \right)} + \frac{\pi\quad D}{n}} = {{D + \frac{\pi\quad D}{n}} = \frac{\left( {n + \pi} \right)D}{n}}}} \\{D_{h} = {\frac{4A}{P} = {\frac{\frac{\pi\quad D^{2}}{n}}{\frac{\left( {n + \pi} \right)D}{n}} = {\left( \frac{\pi}{\pi + n} \right)D}}}} \\{{Re}_{h} = {\frac{\rho\quad{VD}_{h}}{\mu} = {\left( \frac{\pi}{\pi + n} \right)\frac{\rho\quad{VD}}{\mu}}}}\end{matrix}$

where D is the inside diameter of the nozzle 99 and n is the number ofequally sized, semicircular, wedge-shaped channels 109. Comparing theReynolds number of the nozzle 99 with the channels 109 to the nozzle 99not containing any flow-straightening channels yields the followingratio:$\frac{{Re}_{h}}{Re} = {\frac{\left( \frac{\pi}{\pi + n} \right)\frac{\rho\quad{VD}}{\mu}}{\frac{\rho\quad{VD}}{\mu}} = \frac{\pi}{\pi + n}}$

Thus, the Reynolds number of liquid flowing through the nozzle assembly38 with the flow-straightening channels 109 has been reduced by a factorof (π)/(π+n) as compared to a nozzle assembly 38 withoutflow-straightening channels in place. As indicated, increasing thenumber of channels 109 would further decrease the Reynolds number of theliquid flowing through the nozzle 99. Additionally, the surfaces 110 ofeach flow-straightening channel 109 increase the available surface areaupon which viscous forces acting between the liquid and the surfaces 110can form, thereby further decelerating the liquid as it travels throughthe nozzle 99.

The nozzle assembly 38 may be insulated and/or cooled by liquid or othermeans known in the art, including, but not limited to foam, air,circulated glycol, circulated water and thermoelectric means. Since thenozzle assembly 38 is exposed to the ambient air, it may warm to theambient temperature in the absence of such insulation or coolingmechanism. Extending the glycol lines of a glycol-cooled dispensingsystem such that they coil within the nozzle assembly 38 (not shown) maybe used to keep the nozzle assembly 38 cold.

A principal cause of excessive foaming when dispensing beer is havingthe beverage hit the bottom of the container at a great velocity or inan otherwise turbulent manner. Flow redirector 100 minimizes foaming bygently redirecting and dispersing liquid exiting the nozzle assembly 38in a manner that reduces the force of impact between the liquid and thecontainer. As shown by simulated liquid flow lines 96 in FIG. 18, liquidtraveling through the nozzle assembly 38 is evenly dispersed around theflow redirector shaft 106. As liquid flows past the flow redirector 100,it is gently redirected from flowing in a generally downward directioninto flowing in a radial direction. Preferably, liquid exiting thenozzle assembly 38 is dispersed radially, in an even 360-degree patternthat also possesses a downward vector. Such a pattern has beendetermined to minimize foaming of the beverage as it is dispensed for awide variety of container sizes. A lip 111 at the lower end of nozzle 99may also be present. Lip 111 is preferably rounded, although othershapes are contemplated, so as to improve the flow characteristics ofliquid exiting the nozzle assembly outlet 105.

Preferably, flow redirector 100 is a streamlined object. In a preferredembodiment, the proximal end 112 of flow redirector 100 is in the shapeof an elliptical dome. In this embodiment, a round flow redirector shaft106 gradually widens towards the flow redirector base 113 so as toredirect the liquid flow with the least amount of turbulence.Preferably, the horizontal cross-section along the entire longitudinallength of the flow redirector 100 is circular, although other shapes, aslong they do not substantially interfere with the flow of the liquid,are contemplated. The flow redirector base 113 is also preferablycircular and flat such that the bottom of a flat-bottomed container canbe positioned flush against the flow redirector base 113. However, thebottom of flow redirector base 113 may also have a somewhat concavesurface as long as the peripheral edge of the bottom of the flowredirector base 113 substantially contacts the bottom of the containerto be filled. The exterior surface of the flow redirector 100 ispreferably smooth.

While a tall, wide flow redirector 100 would serve to decrease theturbulence caused when redirecting the liquid, such a flow redirector100 would result in a long, wide nozzle assembly 38 that would havedifficulty fitting into smaller containers. For this reason, a morecompact flow redirector 100 is desirable. Preferably, the flowredirector 100 is between 0.5 inches (1.27 cm) and 8 inches (20.32 cm)when measured between its proximal end 112 and its base 113. Morepreferably, the flow redirector 100 is between 1 inch (2.54 cm) and 4inches (10.16 cm) when measured along this length. Still morepreferably, the flow redirector 100 is 2 inches (5.08 cm) when measuredalong this length. Preferably, the flow redirector base 113 measuresbetween 0.25 inches (0.635 cm) and 5 inches (12.7 cm) at its widestpoint. More preferably, the flow redirector base 113 measures between0.5 inches (1.27 cm) and 2 inches (5.08 cm) at its widest point.Additional embodiments of flow redirector 100 are illustrated in FIG.20, FIG. 21, and FIG. 22. Many other flow redirector 100 shapes andconfigurations are possible that accomplish the task of reducing theamount of foaming caused when the liquid leaves the nozzle assembly 38and impacts a container. Preferably, the flow redirector is obconical.

Preferably, flow redirector 100 is generally not movable, but isremovable. Flow redirector 100 may be attached to the inside of thenozzle 99 via one or more support structures 114. Support structures 114are of sufficient strength to hold the flow redirector 100 centeredalong the axis of the nozzle 99, even in the presence of a liquidstream. To minimize their disturbance to liquid flow, support structures114 are preferably streamlined and comprise a rounded proximal end 115that gradually tapers to a point at the distal end 116. An airfoilshape, as shown in FIG. 19, has been found to minimize the turbulencecaused by the support structures 114. In the case of a nozzle assembly38 that contains flow-straightening channels 109, flow redirector 100may not require support structures 114 to hold it in place as it may beaffixed directly to the surfaces 110 forming the flow-straighteningchannels 109.

Flow redirector 100 is positioned longitudinally within the nozzleassembly 38 such that a nozzle assembly outlet 105 is formed between thelip 111 of the nozzle assembly 38 and the flow redirector 100 thatallows liquid to leave the nozzle assembly 38 and enter the container.The size of the nozzle assembly outlet 105 must be large enough to allowliquid to rapidly exit the nozzle assembly 38, and small enough toobtain an even, radial dispersion of liquid into the container. Theoptimal size of the nozzle assembly outlet 105 varies with liquid flowrate, nozzle 99 diameter and the particular shape of the flow redirector100. Preferably, the height of the nozzle assembly outlet 105 asmeasured as the vertical distance between the lip 111 of the nozzle 99and flow redirector 100 is between 0.2 inches (0.508 cm) and 1.5 inches(3.81 cm). More preferably, the height of the nozzle assembly outlet 105is between 0.35 inches (0.889 cm) and 0.6 inches (1.524 cm). Still morepreferably, the height of the nozzle assembly outlet 105 is between 0.4inches (1.016 cm) and 0.5 inches (1.27 cm).

While the height of the nozzle assembly outlet 105 may be a fixeddistance, another embodiment of this invention, shown in FIG. 23 andFIG. 24, allows for fine-tuning of the specific longitudinal position ofthe flow redirector 100 within the nozzle assembly 38 via set screws 117and countersunk slots 118 in the nozzle 99 allowing for longitudinalmovement of the flow redirector 100 upon loosening the set screws 117.In moving the flow redirector 100 longitudinally along the axis of thenozzle assembly 38, the height of the nozzle assembly outlet 105 ischanged. The set screws 117 may also be completely removed from thenozzle assembly 38 such that the flow redirector 100 can be removed fromthe nozzle assembly 38 for cleaning or maintenance purposes.

In another embodiment of this invention, a diffuser 121 is placedupstream from the valve assembly 37 so as to increase the crosssectional area of liquid entering the valve assembly 37 in a manner thatminimizes the amount of turbulence. Preferably, the diffuser 121 tapersfrom its throat end 119 to its exit end 120. In one embodiment, shown inFIG. 25, a conical diffuser 121 is positioned within the neck assembly36 of the rapid beverage dispensing device 35. The axis of the conicaldiffuser 121 in this embodiment is aligned vertically within the neckassembly 36 of the rapid beverage dispense device 35, although it mayalso posses a radius of curvature. Preferably the divergence angle ofthe conical diffuser 121, as measured as the angle between thelongitudinal axis of the conical diffuser 121 and the conical diffuserwall 122, is relatively small. A large divergence angle typicallyresults in increased turbulence as the liquid is forced to expand incross-sectional area over a short distance. To facilitate diffusionwhile minimizing turbulence, preferably the conical diffuser 121possesses a divergence angle of fewer than 25 degrees. More preferably,the divergence angle is fewer than 12 degrees, and even more preferablyis 8 or fewer degrees.

Under certain conditions, it may be desirable to slow the flow rate ofthe liquid leaving the rapid beverage dispensing device 35. In anotherembodiment of the present invention, shown in FIG. 26, apressure-reducing element 123 is introduced into this system inconjunction with a multi-way valve 124 in order to optionally slow theflow rate of the liquid being dispensed. While a pressure-reducingelement 123 can take many forms, preferably, the pressure-reducingelement 123 consists of a length of narrow diameter tubing. Thepressure-reducing element 123 is coiled within the neck assembly 36 ofthe rapid beverage dispensing device 35 so as to minimize its spacerequirements.

The inbound end 125 and outbound end 126 of the pressure-reducingelement 123 are connected to a multi-way valve 124 positioned at theneck base 127 of the rapid beverage dispensing device 35. As shown inone embodiment in FIG. 27, in one position, the multi-way valve 124provides an unimpeded, full-port opening between the rapid beveragedispensing device 35 and the rest of the beer dispensing system 39.Liquid flow arrows 128 indicate the path of liquid flow through themulti-way valve 124. In this position, the liquid flow completely bypasses the pressure-reducing element 123 and liquid is dispensed fromthe rapid beverage dispensing device 35 at its normal flow rate as ifthe pressure-reducing element 123 were not present.

As shown in FIG. 28, in its other position, the multi-way valve 124directs liquid through the pressure-reducing element 123 on its waythrough the rapid beverage dispensing device 35. In this position,liquid entering the multi-way valve 124 is directed to the outboundvalve port 129 which is attached to the inbound end 125 of thepressure-reducing element 123. Energy from the beer dispensing system 39continues to move the liquid through the entire length of thepressure-reducing element 123 before the liquid re-enters the multi-wayvalve 124 through its inbound valve port 130 which directs the liquidfrom the outbound end 126 of the pressure-reducing element 123 throughthe rapid beverage dispensing device 35. Because the liquid re-enteringthe multi-way valve 124 has experienced a drop in pressure, the liquidre-enters the rapid beverage dispensing device 35 at a reduced flowrate, preferably the optimal flow rate of a conventional beer dispensingfaucet.

It is therefore intended that the foregoing detailed description beregarded as illustrative rather than limiting, and that it be understoodthat it is the following claims, including all equivalents, that areintended to define the spirit and scope of the invention.

1. A method for decreasing the formation of foam in carbonated beverages comprising: directing the flow of liquid to a liquid dispensing nozzle having a liquid flow control valve having an open position and a closed position, a liquid receiving opening, a liquid dispensing opening, and a liquid flow path of decreasing cross-section; positioning the bottom of the inside of a liquid receiving receptacle near the opening of the nozzle; moving the valve to the open position to permit the flow of the liquid through the nozzle; directing the flow of liquid through the nozzle to the fluid dispensing opening in a path generally parallel to the nozzle; and redirecting the flow of liquid by means of a liquid flow redirector at the opening of the nozzle in a direction generally tangential to the liquid receiving receptacle. 